US8739945B2 - Disc brake adjusting device having an output side coupling ring with a defined working rotational angle - Google Patents
Disc brake adjusting device having an output side coupling ring with a defined working rotational angle Download PDFInfo
- Publication number
- US8739945B2 US8739945B2 US13/015,974 US201113015974A US8739945B2 US 8739945 B2 US8739945 B2 US 8739945B2 US 201113015974 A US201113015974 A US 201113015974A US 8739945 B2 US8739945 B2 US 8739945B2
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- US
- United States
- Prior art keywords
- drive
- clutch
- ring
- disc
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/38—Slack adjusters
- F16D65/40—Slack adjusters mechanical
- F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
- F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
- F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
- F16D65/568—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake for synchronous adjustment of actuators arranged in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/38—Slack adjusters
- F16D65/40—Slack adjusters mechanical
- F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
- F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
Definitions
- the invention relates to an adjusting device for a disc brake and, in particular, an adjusting device for a pneumatically actuated disc brake.
- the adjusting device adjusts for wear of the brake pads and the brake disc of a pneumatically actuated disc brake having a rotary-lever-actuated brake application device, which adjusting device can preferably be inserted into an adjusting spindle of the disc brake and attached to a brake caliper of the disc brake by way of a bearing disc.
- Adjusting devices or wear adjustors for disc brakes exist in various embodiments.
- DE 10 2004 037 771 A1 discloses an adjusting device for a disc brake, the specifications of which are expressly incorporated by reference herein.
- This adjusting device is suitable for a pneumatically actuated disc brake, in particular one of sliding-caliper design.
- the adjusting device can, however, also be used in pneumatically actuated fixed-caliper or pivoting-caliper disc brakes.
- Pneumatically actuated disc brakes have over time become standard equipment on heavy commercial vehicles. Such disc brakes require mechanical boosting or “force amplification” in order to produce the demanded brake application force, because the force of the pneumatically charged brake cylinders is restricted on account of the pressure level (at present approximately 10 bar) and the limited structural size of the brake cylinder.
- Presently known pneumatically actuated disc brakes have boost ratios of between 10:1 and 20:1.
- the piston strokes of the brake cylinders are in the range from 50 mm to 75 mm, resulting in brake application travels of approximately 4 mm for pressing the brake pads against the brake disc.
- the friction material thickness of the brake pads lies in the range of 20 mm, and because two pads are installed, this results in a wear travel of approximately 40 mm, not taking disc wear into consideration. This travel is a multiple greater than the abovementioned brake application travel. It is therefore necessary for the brake to be adjusted correspondingly to the pad wear by way of a device.
- the prior art provides automatic wear adjustment by way of which the so-called air play, that is to say the gap between the brake pads and the brake disc in the non-actuated state, is kept constant independently of the wear state and wear behavior of the brake pads.
- DE 10 2004 037 711 A1 describes an adjuster of the type, which is shown in FIG. 5 .
- the adjuster is composed substantially of the following functional elements: shaft 2 ; bearing disc 3 ; axial bearing 5 ; collar bush, or spacer sleeve 19 ; shift fork, or drive ring 6 ; ball ramp clutch 7 ; cone clutch 17 ; and cylindrical spring 12 .
- shaft 2 bearing disc 3
- axial bearing 5 axial bearing 5
- collar bush, or spacer sleeve 19 shift fork, or drive ring 6
- ball ramp clutch 7 ball ramp clutch 7
- cone clutch 17 cone clutch 17
- cylindrical spring 12 With regard to the description, reference is made to DE 10 2004 037 711 A1.
- the adjusting device must basically perform two functions:
- the adjusting device When being turned back, for example to replace the brake pads, the adjusting device is turned back or retracted by hand using a screwdriver from its so-called wear position into its initial position.
- the adjusting device must be turned counter to the blocking direction of the freewheel. Since the freewheel however has a 100% blocking action, turning back cannot be carried out without special design measures.
- an adjusting device for adjusting for wear of the brake pads and the brake disc of a pneumatically actuated disc brake having a rotary-lever-actuated brake application device which adjusting device can preferably be inserted into an adjusting spindle of the disc brake and attached to a brake caliper of the disc brake by way of a bearing disc.
- An axial bearing is formed axially on one side of a drive ring and a ball ramp clutch with freewheel function is formed axially on the opposite side of the drive ring.
- the ball ramp clutch has balls, a drive bush arranged at the drive input side axially between the axial bearing and the balls thereof and a drive-output-side clutch ring.
- a cone clutch is arranged between the drive-output-side clutch ring and a spring sleeve for a cylindrical spring.
- the drive-output-side clutch ring is designed for a working angle of rotation as limited by at least one stationary stop.
- the working angle of rotation is to be understood to mean the angle of rotation by which the adjusting device is rotated in the event of an automatic adjustment process during a braking process.
- a directional clutch which acts in the axial direction is installed in this adjusting device.
- the directional clutch is formed from a ball ramp system and a friction clutch, in particular a ball-cone clutch.
- the bore of the clutch ring therefore has a profiling, by which the ring is prevented from turning back in the so-called rest position of the adjuster.
- the clutch ring is supported on a stop, preferably on a stop of the rotationally fixedly mounted collar bush, which has an external profiling matching the internal profiling of the clutch ring.
- the two profilings are coordinated with one another such that the clutch ring has the clearance necessary for the working angle of rotation for the automatic air play adjustment.
- the stop is integrally formed on an end section of a collar bush which extends axially through the ball ramp clutch and through the drive-output-side clutch ring, the other end of which collar bush has a collar which forms a stationary section of the axial bearing.
- the cone clutch is preferably a ball-cone clutch which has the drive-output-side clutch ring and a tapered bush which is connected to the spring sleeve. Clamping balls are arranged between the drive-output-side clutch ring and the tapered bush.
- the axial bearing is formed by one side of the drive ring, by rolling bodies and by a collar of a collar bush which extends axially through the ball ramp clutch. This likewise reduces the number of different parts and provides a compact design.
- a disc brake in particular pneumatically actuated disc brake, has an adjusting device according to the above description.
- FIG. 1 is a partial section illustration of an exemplary embodiment of an adjusting device according to the invention
- FIG. 2 is an enlarged partial section illustration of the upper region of FIG. 1 ;
- FIG. 3 is a perspective partial section view of the exemplary embodiment according to FIG. 1 ;
- FIG. 4 is an enlarged perspective partial section view taken along X-X in the region of a clutch ring according to FIG. 2 ;
- FIG. 5 is a partial section illustration of an adjusting device according to the prior art.
- FIG. 6 is a schematic illustration of a disc brake.
- FIG. 6 With regard to the design and function of a pneumatic disc brake according to FIG. 6 , reference is made to the corresponding description of DE 197 29 024 C1, the specification of which is expressly incorporated by reference herein.
- the following components are indicated in FIG. 6 : disc brake 20 , brake disc 21 , brake caliper 22 , brake pads 23 , bridge 24 , adjusting spindles 25 and 26 , thrust pieces 27 , sprockets 28 , chain 29 , eccentric 30 and rotary lever 31 , which has a drive element 32 interacting with a shift fork of an adjusting device 1 .
- the adjusting device 1 is in this case arranged in the adjusting spindle 25 .
- An adjusting device 1 will now be explained in more detail.
- the adjusting device 1 would also be suitable for an electromotively actuated disc brake.
- FIG. 1 is a partial section illustration of an exemplary embodiment of an adjusting device 1 according to the invention.
- FIG. 2 illustrates an enlarged partial section illustration of the upper region of FIG. 1
- FIG. 3 shows a perspective partial section illustration of the exemplary embodiment according to FIG. 1 .
- the adjusting device 1 has the following: a shaft 2 , having a drive journal at its upper end; a bearing disc 3 for fastening the adjusting device 1 in the brake caliper 22 (see FIG. 6 ); a collar bush 4 which is rotationally fixedly coupled to the bearing disc 3 and has an upper collar with a running surface arranged therebelow for balls of an axial bearing 5 ; a drive ring 6 which is connected to a shift fork which is coupled to the drive element 32 (see FIG.
- a ball ramp clutch 7 having a clutch ring 8 which interacts with a tapered bush 11 which is connected to a spring sleeve 14 for conjoint rotation therewith; a cylindrical spring 12 which is arranged in the spring sleeve 14 and which is supported on a profiled disc 15 ; and an adjusting element 16 , for example a nut, which is arranged on the lower end of the shaft 2 and serves for stressing the cylindrical spring 12 and holding the elements of the adjusting device 1 together axially.
- the ball ramp clutch 7 is composed of a drive bush 33 , which is a lower section of the drive ring 6 , balls or rolling bodies, and the clutch ring 8 , with the clutch ring 8 having an upper section for receiving the balls and a lower section which forms a part of the cone clutch 17 .
- the general function of the adjusting device 1 is described in detail in DE 10 2004 037 771 A1 with regard to FIG. 5 , to which reference is hereby made.
- the axial bearing 5 is formed from the collar of the collar bush 4 , from one side of the drive ring 6 and from rolling bodies.
- the lower end of the collar bush 4 which extends through the ball ramp clutch 7 forms, directly or via a thrust washer, an axial stop 9 for the tapered bush 11 .
- the tapered bush 11 is pressed upward by the cylindrical spring 12 via the spring sleeve 14 , with the cone clutch 17 , ball ramp clutch 7 and axial bearing 5 components being held together and pressed together axially.
- the collar bush 4 with its stop serves to maintain a minimum play of the bearing arrangements.
- a significant difference in relation to the prior art consists in that the drive-output-side clutch ring 8 has only a limited angle of rotation, specifically a limited working angle of rotation ⁇ A , which will be explained in more detail in FIG. 4 .
- the shaft 2 has, at its left-hand end in FIG. 3 , a drive journal 13 which has a corresponding key, for example a hexagonal profiling.
- a tool engaged thereon for example an offset box wrench
- the shaft 2 is now turned clockwise in the direction of the arrow shown.
- the rotational movement is introduced via the shaft 2 and the spring sleeve 14 into the cone clutch 17 . That is to say, via the tapered bush 11 into the clamping balls 10 , and from the latter into the drive-output-side clutch ring 8 .
- the drive-output-side clutch ring 8 bears against a stationary stop 9 ( FIG. 4 ) and can co-rotate no further.
- the clutch ring 8 which is prevented from rotating cannot transmit any rotation to the ball ramp clutch 7 , which is therefore also not adjusted into a transmission position.
- the torque introduced by the box wrench into the shaft 2 can rotate the spring sleeve 14 further, and the rotational movement can be transmitted to the adjusting spindle 25 (not shown) for a restoring movement.
- the region of the stop 9 is shown in FIG. 4 in an enlarged partial section view (line X-X in FIG. 2 in the region of the clutch ring 8 ).
- the collar bush 4 has an elongated lower end ( FIG. 2 ) which extends axially through the ball ramp clutch 7 into the clutch ring 8 and which, in the region, is provided with an external profile 36 .
- the external profile 36 extends radially outward and is designed for example in the form of a sector of a circle.
- the external profiling 36 is arranged symmetrically and interacts with a corresponding internal profiling 35 of the surrounding clutch ring 8 .
- intermediate spaces are arranged on the circular circumference of the internal profile 35 and external profile 36 , which intermediate spaces define the working angle of rotation ⁇ A .
- the clutch ring 8 can therefore rotate by the working angle ⁇ A , which is defined by the profiling 35 and 36 , during an automatic adjustment.
- the external profile 36 of the collar bush 4 forms the stop 9 , which prevents a rotational movement of the clutch ring 8 driven by a restoring wrench.
- the locking of the collar bush 4 is provided by way of the bearing disc 3 fastened to the brake caliper 22 , by virtue of bent lugs of the bearing disc 3 engaging into radial recesses on the circumference of the collar of the collar bush 4 .
- the locking of the collar bush 4 may take place directly on the brake caliper 22 , for example by way of cams and corresponding recesses in the brake caliper 22 .
- the internal and external profiles 35 , 36 may also have other shapes.
- Adjusting device 2 Shaft 3 Bearing disc 4 Collar bush 5 Axial bearing 6 Drive ring 7 Ball ramp clutch 8 Clutch ring 9 Stop 10 Clamping balls 11 Tapered bush 12 Cylindrical spring 13 Drive journal 14 Spring sleeve 15 Profiled disc 16 Adjusting element 17 Cone clutch 18 Sleeve cone 19 Spacer sleeve 20 Disc brake 21 Brake disc 22 Brake caliper 23 Brake pads 24 Cross-member (bridge) 25 First adjusting spindle 26 Second adjusting spindle 27 Thrust piece 28 Sprockets 29 Chain 30 Eccentric 31 Rotary lever 32 Drive element 33 Drive bush 35 Internal profile 36 External profile ⁇ A Working angle of rotation
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008035366 | 2008-07-30 | ||
DEDE102008035366.3 | 2008-07-30 | ||
DE102008035366A DE102008035366A1 (de) | 2008-07-30 | 2008-07-30 | Nachstellvorrichtung für eine Scheibenbremse |
PCT/EP2009/005411 WO2010012429A2 (de) | 2008-07-30 | 2009-07-27 | Nachstellvorrichtung für eine scheibenbremse |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2009/005411 Continuation WO2010012429A2 (de) | 2008-07-30 | 2009-07-27 | Nachstellvorrichtung für eine scheibenbremse |
Publications (2)
Publication Number | Publication Date |
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US20110203884A1 US20110203884A1 (en) | 2011-08-25 |
US8739945B2 true US8739945B2 (en) | 2014-06-03 |
Family
ID=41461454
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/015,974 Active 2030-03-04 US8739945B2 (en) | 2008-07-30 | 2011-01-28 | Disc brake adjusting device having an output side coupling ring with a defined working rotational angle |
Country Status (8)
Country | Link |
---|---|
US (1) | US8739945B2 (pt) |
EP (1) | EP2307755B1 (pt) |
JP (1) | JP5628801B2 (pt) |
CN (1) | CN102112773B (pt) |
BR (1) | BRPI0916740B1 (pt) |
DE (1) | DE102008035366A1 (pt) |
RU (1) | RU2495291C2 (pt) |
WO (1) | WO2010012429A2 (pt) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150068852A1 (en) * | 2012-05-18 | 2015-03-12 | Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh | Wear Adjustment Device of a Disc Brake and Corresponding Disc Brake |
US10935115B2 (en) | 2018-08-20 | 2021-03-02 | Hamilton Sunstrand Corporation | Linear actuator with testable cone no-back and torque limiter |
US10982728B2 (en) * | 2016-03-24 | 2021-04-20 | Bpw Bergische Achsen Kg | Adjustment mechanism for a vehicle disk brake as well as a cardanic rotary bearing and a coupling ring therefor |
US11365775B2 (en) * | 2018-04-12 | 2022-06-21 | Shandong Toget Brake System Co., Ltd | Commercial vehicle air disc brake caliper assembly |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008048922A1 (de) * | 2008-09-26 | 2010-04-01 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Nachstellvorrichtung für eine Scheibenbremse |
CN101526116B (zh) * | 2009-03-24 | 2012-03-07 | 隆中控股集团有限公司 | 一种汽车自动调整臂 |
GB201105236D0 (en) | 2011-03-29 | 2011-05-11 | Meritor Heavy Vehicle Braking | A brake adjuster mechanism |
DE102011117587A1 (de) * | 2011-11-03 | 2013-05-08 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Nachstellvorrichtung für eine Scheibenbremse |
DE102012108682A1 (de) * | 2012-09-17 | 2014-03-20 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Scheibenbremse mit einer Synchroneinrichtung |
DE102012108676B3 (de) * | 2012-09-17 | 2014-02-06 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Scheibenbremse mit einer Verschleißnachstellvorrichtung |
DE102013100786A1 (de) * | 2013-01-25 | 2014-07-31 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Scheibenbremse mit einer Lüftspielüberwachungsvorrichtung und Verfahren zur Lüftspielüberwachung |
DE102013016882B4 (de) * | 2013-10-11 | 2020-07-09 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Nachstellvorrichtung einer Scheibenbremse |
CN105276040A (zh) * | 2014-05-29 | 2016-01-27 | 枣庄泰德机械有限公司 | 一种链条传动式高档客车制动间隙从动调整机构及制造方法 |
DE102014113055B4 (de) | 2014-09-10 | 2023-03-23 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Scheibenbremse mit einer Nachstellvorrichtung |
CN104763761A (zh) * | 2015-04-10 | 2015-07-08 | 江苏佰瑞克汽配有限公司 | 一种汽车盘式制动器主自调机构总成 |
CN107542802B (zh) * | 2017-09-01 | 2020-03-31 | 杭州富阳新远新能源有限公司 | 一种基于齿牙传动的离合器 |
US20220356922A1 (en) * | 2019-09-17 | 2022-11-10 | Zf Cv Systems Europe Bv | Brake caliper and spring unit for a brake caliper |
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DE3341059A1 (de) | 1983-11-12 | 1985-05-23 | Hans-Henning Prof. Dr.-Ing. 6100 Darmstadt Lüpertz | Automatische nachstelleinrichtung fuer mechanische zuspanneinrichtungen vornehmlich fuer scheibenbremsen |
GB2192033A (en) | 1986-06-28 | 1987-12-31 | Teves Gmbh Alfred | Disc brake for motor vehicles |
US5353896A (en) * | 1990-06-07 | 1994-10-11 | Knorr-Bremse Systeme Feur Nutzfahrzuege | Disk brakes for motor vehicles |
US6213255B1 (en) * | 1998-04-02 | 2001-04-10 | Ina Walzlager Schaeffler Ohg | Adjusting device for disk brakes |
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2008
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2009
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- 2009-07-27 CN CN200980129739XA patent/CN102112773B/zh active Active
- 2009-07-27 BR BRPI0916740A patent/BRPI0916740B1/pt active IP Right Grant
- 2009-07-27 WO PCT/EP2009/005411 patent/WO2010012429A2/de active Application Filing
- 2009-07-27 EP EP09777446A patent/EP2307755B1/de active Active
- 2009-07-27 RU RU2011107723/11A patent/RU2495291C2/ru active
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2011
- 2011-01-28 US US13/015,974 patent/US8739945B2/en active Active
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150068852A1 (en) * | 2012-05-18 | 2015-03-12 | Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh | Wear Adjustment Device of a Disc Brake and Corresponding Disc Brake |
US10982728B2 (en) * | 2016-03-24 | 2021-04-20 | Bpw Bergische Achsen Kg | Adjustment mechanism for a vehicle disk brake as well as a cardanic rotary bearing and a coupling ring therefor |
US11365775B2 (en) * | 2018-04-12 | 2022-06-21 | Shandong Toget Brake System Co., Ltd | Commercial vehicle air disc brake caliper assembly |
US10935115B2 (en) | 2018-08-20 | 2021-03-02 | Hamilton Sunstrand Corporation | Linear actuator with testable cone no-back and torque limiter |
Also Published As
Publication number | Publication date |
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RU2495291C2 (ru) | 2013-10-10 |
RU2011107723A (ru) | 2012-09-10 |
JP2011529556A (ja) | 2011-12-08 |
DE102008035366A1 (de) | 2010-02-04 |
WO2010012429A2 (de) | 2010-02-04 |
CN102112773A (zh) | 2011-06-29 |
EP2307755B1 (de) | 2012-09-19 |
JP5628801B2 (ja) | 2014-11-19 |
BRPI0916740A2 (pt) | 2015-11-03 |
WO2010012429A3 (de) | 2010-04-29 |
CN102112773B (zh) | 2013-09-18 |
BRPI0916740B1 (pt) | 2020-04-28 |
US20110203884A1 (en) | 2011-08-25 |
EP2307755A2 (de) | 2011-04-13 |
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